Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
  • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
  • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
  • F03G7/05—Ocean thermal energy conversion, i.e. OTEC
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C1/00—Rotary-piston machines or engines
  • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C19/00—Sealing arrangements in rotary-piston machines or engines
  • F01C19/02—Radially-movable sealings for working fluids
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/08—Rotary pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K15/00—Adaptations of plants for special use
  • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/06—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using mixtures of different fluids
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
  • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
  • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
  • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2210/00—Fluid
  • F04C2210/10—Fluid working
  • F04C2210/1066—Nitrogen (N2)
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E10/00—Energy generation through renewable energy sources
  • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

• the invention relates to the field of new energy sources. It is a type of cold state engine or apparatus that can conveniently and efficiently use air thermal energy to output work, refrigeration and water, especially comprising "Cryogenic Working Fluid Thermodynamic - Refrigeration Cycle", “Frost-Free Two Stage Cycle Heat Exchange” and other fundamental methods, as well as “High Pressure Expander” and other key device.
• the atmosphere is a low temperature heat reservoir, with considerable atmospheric thermal energy. Atmospheric thermal energy mainly comes from solar energy, followed by geothermal energy and the dissipation of waste heat into the atmosphere from various human energy consumption activities (such as use of coal, gas, oil, electricity etc). Therefore the atmosphere can said to be an almost inexhaustible "sea of energy”.
• thermodynamics theory methods and devices can not take advantage of the environmental heat energy from this considerable and ever present energy reservoir to do work or output electrical energy.
• the invention consists in a cold state engine or apparatus for use in utilising air heat energy to output mechanical work, refrigerated air and water in a two stage cycle comprising first stage cycle components and second stage cycle components, the first stage cycle components comprising:
• a working fluid pump disposed between the expander and the vaporiser
• the second stage cycle components comprising:
• the apparatus comprises a storage tank that is disposed between the vaporizer and the expander wherein the storage tank and is fluidly and operatively connected to the vaporizer and the expander.
• the storage tank comprises thermometer and pressure meter adapted to measure the temperature and pressure respectively.
• the components are fluidly connected by connecting means which includes piping.
• the vaporiser includes a cylindrical shell shaped vessel having vertically oriented tubes having at least two inlets and at least two outlets wherein one of the inlets is fluidly and operatively connected from the working fluid pump, and the other inlet is fluidly and operatively connected from the ambient air heat exchanger and one of the outlets is fluidly and operatively connected to the expander and the other outlet is fluidly and operatively connected to the circulation pump.
• the vaporiser includes a safety valve and a release valve.
• connection means includes at least one thermometer and pressure meter adapted to measure the temperature and pressure respectively.
• connection means includes a one way valve.
• the expander, the working fluid pump and the piping between them have at least one insulation layer on their exterior.
• the ambient air heat exchanger includes a housing having a tubular structure adapted to circulate cold heat transfer liquid and a fan adapted to draw air past the circulating cold heat transfer liquid to cause the cold heat transfer liquid to warm up.
• the expander is connected to a generator that is capable of using the mechanical work output of the expander to generate power.
• the expander which is for producing mechanical work from a working fluid comprises:
• cylindrical casing with an inlet and an outlet for the working fluid
• a cylindrical piston wheel including at least one circle of piston chamber, the piston chamber being circumferentially located surrounding the piston shaft; the outer circumference of the at least one piston chamber having sealing ring grooves with at least one band shaped sealing ring having at least one aperture located between the sealing ring grooves;
• the cylindrical casing houses the cylindrical piston wheel and the band shaped sealing ring(s) and the piston chamber is mounted on the piston shaft such that when the piston chamber is moved by the working fluid inside the casing, mechanical work can be produced.
• the expander further comprising three piston chambers being connected by a connection tube located in the or each piston chamber and the connection tube being adapted to obtain sufficient displacement for the expander's isometric working process.
• both the inlet and outlet comprise a structure have a base and entry or exit port whereby the base connects the casing of the expander at a tangent and is larger diameter than the diameter of the inlet port and exit port.
• the at least one band shaped sealing ring is formed by multiple seal links, each seal link having a substantially rectangular aperture and each seal link being connected to the other using joints or connectors.
• the at least one band shaped sealing ring is a one piece split ring having two ends connected by joints or connectors.
• the joint or connectors are in the form of mortise and tenons.
• each of the at least two piston chamber having a sealing ring groove on which the band shape sealing ring is fitted.
• the outer circumferential surface of each of the band shaped sealing ring is substantially same as the inner circumferential surface of the casing and the inner circumferential surface of each of the band shaped sealing ring is same as the outer circumferential surface of the sealing ring groove defined by the piston chamber.
• each of the band shaped sealing ring tightly abuts the inner circumferential surface of the casing and the inner circumferential surface of each of the band shaped sealing ring tightly abuts the outer circumferential surface of the sealing ring groove defined by the piston chamber.
• the invention consists in a method of utilizing air heat energy to output mechanical work, refrigerated capacity and water in a two stage cycle, using the apparatus comprising a first cycle components and a second cycle components as described above,
• the first stage cycle components comprising:
• a working fluid pump for pumping the cryogenic working fluid from the expander to the vaporiser, the working fluid pump being disposed between the expander and the vaporiser;
• second stage cycle components comprising:
• an ambient heat exchanger for exchanging heat from the ambient air
• a circulation pump for disposed between the vaporiser and the ambient heat exchanger
• the expander, the vaporiser, the working fluid pump, the ambient heat exchanger and the circulation pump are fluidly and operatively connected together; wherein, the method comprises the first stage cycle and a second stage cycle;
• cryogenic working fluid is heated to a vapour state and transformed to a high pressure vapour state as a high pressure working vapour;
• the high pressure working vapour being transferred to the expander where it is used to output work and refrigeration capacity thereby, causing a decrease in the temperature of the working vapour and liquefied back to a liquid state as a cryogenic working fluid;
• cryogenic working fluid is then pumped backed to the vaporiser using the working fluid pump;
• a cold heat transfer liquid is pumped from the vaporiser to the ambient heat exchanger where the heat transfer liquid exchanges heat with the ambient air causing the temperature of air to decrease and thereby cause the temperature of the cold heat transfer liquid to increase and change to a warm heat transfer liquid;
• the warmed heat transfer liquid is then circulated to the vaporiser to cause the temperature of the cryogenic working fluid in the vaporiser to increase thereby causing the temperature of the warm heat transfer liquid to decrease and change back to the cold heat transfer liquid.
• the second stage cycle occurs initially before the first stage cycle and then occurs at the same time.
• the heat transfer liquid from the ambient air heat exchanger includes water.
• the heat transfer liquid includes water based anti-freeze.
• the cryogenic working fluid is a single atom gas such as such as N2, He-4 or is a mixture of such gases such as air or atom gas such as C02.
• the expander outputs mechanical work and because of the dissipation effect the work becomes a waste heat into the atmosphere, thereby realising a recycling of heat energy.
• the ambient air heat exchanger produces a large amount of condensation, which can be collected and purified as fresh water, thereby enabling the ambient air heat exchanger to make water.
• the moisture in the air condenses and the air turns into the dry air, thereby enabling the ambient air heat exchanger to function as a dehumidifier.
• the invention consists in an expander for producing mechanical work from a working fluid, comprising:
• cylindrical casing with an inlet and outlet for the working fluid
• a cylindrical piston wheel including at least one circle of piston chamber, the piston chamber being circumferentially located surrounding the piston shaft;
• the outer circumference of the at least one piston chamber having sealing ring grooves with at least one band shaped sealing ring having at least one aperture located between the grooves;
• the cylindrical casing houses the cylindrical piston wheel and the band shaped sealing ring(s) and the piston chamber is mounted on the piston shaft such that when the piston chamber is moved by the working fluid inside the casing, mechanical can be produced.
• the expander further comprises three piston chambers being connected by a connection tube located in the or each piston chamber and the connection tube being adapted to obtain sufficient displacement for the expander's isometric working process.
• both the inlet and outlet comprise a structure have a base and entry or exit port whereby the base connects the casing of the expander at a tangent and is larger diameter than the diameter of the inlet port and exit port.
• the at least one band shaped sealing ring is formed by multiple seal links, each seal link having a substantially rectangular aperture and each seal link being connected to the other using joints or connectors.
• the at least one band shaped sealing ring is a one piece split ring having two ends connected by joints or connectors.
• the joint or connectors are in the form of mortise and tenons.
• each of the band shaped sealing ring is substantially same as the inner circumferential surface of the casing and the inner circumferential surface of each of the band shaped sealing ring is same as the outer circumferential surface of the sealing ring groove defined by the piston chamber.
• each of the band shaped sealing ring tightly abuts the inner circumferential surface of the casing and the inner circumferential surface of each of the band shaped sealing ring tightly abuts the outer circumferential surface of the sealing ring groove defined by the piston chamber.
• the invention consists in cold state engine or an apparatus utilising air heat energy to output work, refrigeration and water, comprises at least a vaporiser, high pressure expander, high pressure working fluid pump, ambient heat exchanger, circulation pump, generator, pipes, valves, sensors which are fluidly and operatively interconnected together, using single or two atom gases as a working substance, based on methods of cryogenic working fluid thermodynamic - refrigeration cycle and frost- free two stage cycle heat exchange technology wherein the single fill of cryogenic working fluid or high pressure gas as initial power to start the cycle, absorbs air thermal energy vaporise into high pressure gas which then propels the expander to turn and output mechanical work and refrigeration capacity, the air heat exchanger outputs refrigeration, condensation and dry air.
• cryogenic working fluid thermodynamic - refrigeration cycle or the first stage cycle comprises of three main components: vaporiser, high pressure expander, high pressure working fluid pump; and pipes, valves, sensors and various parts operatively connected to form the cycle.
• the cryogenic working fluid thermodynamic - refrigeration cycle or the first stage cycle is comprised of three connected thermodynamic processes, isobaric absorbing heat process by the vaporiser, adiabatic expansion process by the expander and isentropic compression process by the high pressure working fluid pump.
• the at least one vaporiser is used to produce high pressure working vapour and it is installed between the high pressure working fluid pump and the high pressure expander, the shell side of vaporiser flows high pressure working fluid, the tube side flows low pressure heat transfer liquid.
• At least one expander is installed between the vaporiser and the high pressure working fluid pump and the expander's functions are to output mechanical work and refrigeration capacity.
• at least one high pressure working fluid pump is installed between the expander and vaporiser to increase pressure of working fluid leaving the expander and thus pumping the working fluid into the vaporiser.
• a storage tank fluidly connected between the vaporizer and the expander wherein storage tank increases volume and superheat vapour.
• the single atom gas N2, He-4) or a mixture of such gases (such as air) or two atom gases (such as C02) is used as working substance.
• the initial power of start the cycle is a single fill of cryogenic working fluid or high pressure gas.
• the technology used is working substance gas-liquid phase change cycle.
• T2 the liquefying temperature
• using frost-free two stage cycle heat exchange technology is comprised of the first stage cycle and the second stage cycle wherein the vaporiser, expander and the high pressure pump form a first stage cycle, and vaporiser, ambient heat exchanger and circulation pump form a second stage cycle.
• the second stage cycle is coupled with first stage cycle through the vaporiser.
• the second stage cycle uses water or anti-freeze liquid with low freezing point as heat transfer liquid.
• the working temperature of air heat exchanger is achieved through adjusting the flow of circulating heat transfer liquid of the second stage cycle.
• the exterior of the expander, working fluid pump and the connecting pipes between them all have at least one insulation layer to reduce heat transfer.
• high pressure expander output mechanical work which can be directly used to power vehicle, ships, aircraft and various machines, or can be converted into electricity or thermal energy.
• the expander is a high pressure expander that outputs mechanical work, and because of a dissipation effect, the work becomes waste heat into the atmosphere, realising a recycling of heat energy.
• the apparatus can be modified for concentrated and heavy users of power such as steel plants, cement plants etc, using closed thermal energy recycle method.
• the high pressure expander output cryogenic refrigerating capacity (-196 ⁇ -210), using corresponding heat exchange technology and devices to utilise divided stages of refrigerating capacity (air conditioning 20 ⁇ 25°C, refrigeration 4°C, freezing -8 ⁇ -80°C, cryogenic treatments -120 ⁇ -160°C, air liquefaction -196°C ⁇ -210°C) and can be made into various refrigeration devices.
• the apparatus can be designed to be as large or as small as required, can be manufactured to be a portable electricity generator, a large scale power station, or can be manufactured to be a generator equipped for each household to supply power, refrigeration and air conditioning, and water.
• the heat exchanger is an ambient heat exchanger that can produce a large amount of condensation, which can be collected and purified as quality fresh water, therefore the apparatus can be made into air water making device, wherein the fresh water made will be released into the environment after use, then evaporate into the atmosphere, creating a beneficial water cycle.
• the moisture in the air will condense and the air turns into dry air thus it has a dehumidifying function whereby the apparatus can be made into a dehumidifier.
• the apparatus can use the heat energy in bodies of water (such as rivers, lakes and oceans) to do work, thus it can be made into power device to drive ships and submarine.
• bodies of water such as rivers, lakes and oceans
• the high pressure expander consists of a cylindrical case, piston wheel, band- shaped sealing ring, shaft, bearings base, ends and the cylindrical case has an inlet and an outlet for working fluid and series of connection pipes, wherein, the base of the inlet and the outlet should be as large as possible.
• the piston wheel has one or a multitude of circles of beehive shaped chambers as piston chambers and the circles consisting of piston chambers are connected in series to obtain sufficient displacement.
• each piston chamber's volume is designed to be as small as possible and are all equal, and a thrust surface area is designed to be as big as possible.
• the high pressure expander's working displacement length is designed according to when the final pressure (P2) of the expander's outlet is near zero.
• the piston wheel turns inside the cylindrical case, with only one friction surface formed by the interior wall of the case and the exterior surface of the piston wheel.
• each piston chamber has an opening, where there is a groove for a band-shaped self sealing ring installation wherein the band-shaped self sealing ring has a gap of the u- shaped cross-section all perimeter the inside, which has self sealing function.
• the piston chambers includes a band shaped self sealing ring which is installed on the external circumference surface of the piston chambers to be precision matched with the interior wall of the case, self sealing ring and piston wheel are stabilised through key.
• the band shaped self sealing ring is an open ring, the ends have tenon and mortise joint, and on two sides of the tenon have small spring leaves.
• the expander can be used in fields that the pressure energy of the fluid converted into mechanical work or torque.
• the invention consists in, refrigerated capacity and water in a two stage cycle, using the apparatus comprising a first cycle components and a second cycle components as described above, the first stage cycle components comprising:
• a working fluid pump for pumping the cryogenic working fluid from the expander to the vaporiser, the working fluid pump being disposed between the expander and the vaporiser;
• second stage cycle components comprising:
• an ambient heat exchanger for exchanging heat from the ambient air
• a circulation pump for disposed between the vaporiser and the ambient heat exchanger; wherein, the expander, the vaporiser, the working fluid pump, the ambient heat exchanger and the circulation pump are fluidly and operatively connected together; wherein, the method comprises the first stage cycle and a second stage cycle;
• cryogenic working fluid is heated to a vapour state and transformed to a high pressure vapour state as a high pressure working vapour; the high pressure working vapour being transferred to the expander where it is used to output work and refrigeration capacity thereby, causing a decrease in the temperature of the working vapour and liquefied back to a liquid state as a cryogenic working fluid;
• cryogenic working fluid is then pumped backed to the vaporiser using the working fluid pump;
• a cold heat transfer liquid is pumped from the vaporiser to the ambient heat exchanger where the heat transfer liquid exchanges heat with the ambient air causing the temperature of air to decrease and thereby cause the temperature of the cold heat transfer liquid to increase and change to a warm heat transfer liquid;
• the warmed heat transfer liquid is then circulated to the vaporiser to cause the temperature of the cryogenic working fluid in the vaporiser to increase thereby causing the temperature of the warm heat transfer liquid to decrease and change back to the cold heat transfer liquid,
• the expander includes a cylindrical shaped casing including at least one piston wheel located within the casing and three outer cylindrical piston chambers being adapted to receive high pressure working fluid which is then adapted to push and rotate the piston wheel causing mechanical work
• the invention consists in a high pressure expander, wherein the expander includes a cylindrical shaped casing including at least one piston wheel located within the casing and three outer cylindrical piston chambers being adapted to receive high pressure working fluid which is then adapted to push and rotate the piston wheel causing mechanical work.
• the invention consists in a cold state engine or an apparatus utilising air heat energy to output work, refrigeration and water, comprises of vaporiser, high pressure expander, high pressure working fluid pump, ambient heat exchanger, circulation pump, generator, pipes, valves, sensors which are operatively interconnected together, using single or two atom gases as a working substance, based on methods of cryogenic working fluid thermodynamic- refrigeration cycle and frost-free two stage cycle heat exchange technology wherein the single fill of cryogenic working fluid or high pressure gas as initial power to start the cycle, absorbs air heat energy in vaporise into high pressure vapour which then propels the expander to turn and output mechanical work and refrigeration capacity, the air heat exchanger outputs refrigeration, condensation and dry air, producing inexhaustible green and free energy, refrigeration and water.
• the invention provides the following methods and apparatus:
• Figure 1 shows a schematic diagram of a preferred embodiment of the "Cold State Engine” or “Frost - Free Two Stage Cycle Thermodynamic - Refrigeration System” of the present invention.
• Figure 2 is a block diagram showing a first stage cycle and the second stage cycle combined together by a vaporiser to form the cold state engine of Figure 1.
• Figure 3 shows a graphical representation (Pressure vs. Specific Enthalpy) of a cryogenic working fluid thermodynamic-Refrigeration Cycle based on Nitrogen as working fluid.
• Figure 4 is a perspective view of a high pressure expander for use in the first stage cycle of Figure 1.
• Figure 5 shows a perspective view of the piston wheel used in the expander of Figure 1.
• Figure 6 is an axial cross-sectional view of the expander of figure 4 and 5 along A-A axis.
• Figure 7 is an axial cross-sectional view of the expander of figures 4 and 5 along B-B axis.
• Figure 8 is an axial cross-sectional view of the expander of figure 4 and 5 along B-B axis wherein the structure of the expander is slightly different to the one shown in Figure 7.
• Figure 9 (a) is a perspective view if a first type of band shaped sealing ring for use in the piston when of the expander of Figure 4
• Figure 9 (b) is an axial cross-sectional view of the vaporiser of figure 9 (a) along B-B axis.
• Figure 9 (c) is an axial cross-sectional view of the vaporiser of figure 9 (a) along A-A axis.
• Figure 10 (a) is a perspective view if a second type of band shaped sealing ring for use in the piston wheel of the expander of Figure 4.
• Figure 9 (b) is an axial cross-sectional view of the vaporiser of figure 9 (a) along B-B axis.
• Figure 9 (c) is an axial cross-sectional view of the vaporiser of figure 9 (a) along A-A axis.
• Figure 11 (a) is a perspective view of a gasket ring.
• Figure 11 (b) is an axial cross-sectional view of the gasket ring Figure 11(a) along A-A axis.
• Figure 12 (a) is a perspective view of a vaporiser for use in the cold state engine of Figure 1.
• Figure 12 (b) is an axial cross-sectional view of the vaporiser of figure 12 (a) along A-A axis
• Figure 12 (c) is an axial cross-sectional view of the vaporiser of figure 12 (a) along B-B axis DESCRIPTION OF DRAWINGS
• the present invention comprises a "Cryogenic Working Fluid Thermodynamic -
• Refrigeration Cycle hereinafter “a first stage cycle” and “Frost-Free Heat Exchange Cycle” hereinafter “a second stage cycle”.
• the first stage cycle and second stage cycle are coupled together to form a "Frost-Free Two Stage Cycle Thermodynamic - Refrigeration System” hereinafter “Cold State Engine” or “Apparatus”.
• the first stage cycle includes the following components of three main components namely a vaporiser (1), a high pressure expander (4) and at least one high pressure working fluid pump (6). These three components are operatively connected by piping (2) as shown in Figure 1. Also, as it can be seen in Figure 1 , there are other accessories such as at least one valve (3), storage tank (7), thermometer (11), pressure meter (12), safety valve (13), release valve (14), one way valves (15), and generator (5) that are provided. The surface of the expander (4), working fluid pump (6) and the piping in between are coated by insulation layer (16).
• the second stage cycle mainly includes circulation pump (8), ambient heat exchanger (9) and the vaporiser (1) that are connected operatively together by piping (2) as shown in Figure 1.
• the primary purpose of this second stage cycle is to overcome the challenge of frost forming on ambient heat exchanger.
• the secondary purpose of the second stage cycle includes refrigeration, dehumidification and water making capability.
• the two cycles namely the first stage cycle and the second stage cycle are coupled together through the vaporizer (1) to form the "Frost - Free Two Stage Cycle Thermodynamic - Refrigeration System” or “Cold State Engine” or “Apparatus”.
• the vaporiser (1) contains cryogenic working fluids such as liquid nitrogen, liquid air or liquid Carbon dioxide (C0 2 ). Liquid state cryogenic working fluid or high pressure gas is manually filled into the vaporiser (1) from port (14) of the vaporiser (1) to start cycle.
• thermodynamic processes comprised of the following three thermodynamic processes (see Fig 2):
• the cryogenic working fluid in the vaporiser carries out heat exchange with second stage cycle's heat transfer liquid, which absorbs the heat energy in the heat transfer liquid (this is the first stage cycle's heat input, it spontaneously occurs due to the difference in temperature, the heat transfer therefore does not consume work). Then the cryogenic working fluid vaporises into gas and its temperature up to near ambient temperature (T ls 300k) and its pressure up to the set maximum working pressure (Pi, 12Mpa). This high pressure vapours also fills the storage tank and the piping up to valve (3).
• the high pressure vapour inside the vaporiser and storage tank flows the high pressure expander through piping to propel piston wheel, which outputs mechanical work (expansion work, large in specific work).
• mechanical work expansion work, large in specific work.
• its temperature down is directly proportional to its pressure down.
• the gas's liquefaction range e.g. N2, T 2 , 63-76k; P 2 , O.lMpa
• a gas to liquid phase change occurs become a liquid.
• the expander also output excellent refrigeration capacity whilst outputting mechanical work.
• Cryogenic Working fluid enters the high pressure working fluid pump through piping (all the expander, the pump and piping have an insulation layer on the exterior surface).
• the cryogenic working fluid is then pumped into the vaporiser and again carries the isobaric absorbing heat process and expands into high pressure vapour.
• the high pressure working fluid pump consumes energy to work, however liquid state working substance has almost no compressibility and the pressure rises easily.
• Working fluid pump consumes push work, which is low in specific work (according to calculations, it is 5% of the work output by expander). The whole process repeats, thereby forming "a cryogenic working fluid thermodynamic - refrigeration cycle" or "a first stage cycle".
• the second stage cycle is a frost-free heat exchange cycle.
• a heat transfer liquid preferably water or more preferably, a water based antifreeze having freezing point of -50°C is circulated by the circulation pump.
• the antifreeze exchange heat with cryogenic working fluid, the heat is absorbed by cryogenic working fluid.
• Antifreeze's temperature drops to the determined lowest possible temperature (-20 °C).
• the cold antifreeze flows to the heat exchanger and exchanges heat with air. After the air heat energy has been absorbed, the air temperature drops to low temperature (e.g. -20 ° C). Now the cold air released by the air heat exchanger output excellent refrigeration capacity and can be used for various functions.
• a cryogenic working fluid firstly absorbs heat energy when in the vaporiser (1) vaporise and expands into a high pressure vapour.
• This high pressure vapour is then flow through piping (2) into the high pressure expander (4) to propel a piston wheel (not shown) to turn and output mechanical work and refrigeration capacity.
• the pressure energy of the high pressure vapour is converted into mechanical work and occurs adiabatic enthalpy drop, pressure and temperature all down.
• the temperature down is directly proportional to pressure down.
• the second stage cycle is a frost-free heat exchange cycle.
• a heat transfer liquid preferably water or more preferably, a water based antifreeze having freezing point of -50°C is circulated to and into the heat exchanger via circulation pump (8).
• the ambient air enters and goes through the heat exchanger (9) causing air temperature to fall.
• a refrigeration capability is provided.
• the air temperature decreases to a dew point, the air moisture condenses into water which can be collected and purified to be used as high quality fresh water.
• the heat transfer liquid that is circulated to the heat exchanger (9) is also outputted as a warm fluid/liquid and this warm fluid/liquid is circulated back to the vaporiser (1).
• This heat energy of this warm fluid is absorbed by the cryogenic working fluid present inside the vaporiser (1) which vaporises and expands into a high pressure vapour thereby causing the first stage cycle, as explained above, to occur.
• This absorption of heat energy from the warm heat transfer liquid will turn it into cold liquid.
• This cold liquid is circulated to heat exchanger (9) as a heat transfer liquid via the circulation pump and the second cycle repeats.
• the two cycles namely the first stage cycle and the second stage cycle are coupled together through the vaporiser (1) to form the "Frost- Free Two Stage Cycle Thermodynamic - Refrigeration System".
• Liquid state cryogenic working fluid or high pressure gas is manually filled into the vaporiser (1) from port (14) of the vaporiser (1).
• the amount of working fluid filled should be determined by the cycle volume combined from vaporiser (1), storage tank (7), piping (2), so that when the cryogenic working fluid is completely vaporised and expanded, it can only reach the system's maximum working pressure. Even when the high pressure gas is filled into the system through vaporiser (1), it can still only add up to the system's maximum working pressure.
• the initial power (filled cryogenic working fluid or high pressure gas) will always remain in the system (similar to how refrigerant remains in the refrigeration machine for a long time) which can be used to open valves (3) and start operation, and to close valve (3) and turn off the apparatus.
• the degree of opening of the valve (3) directly controls the flow of the working fluid thereby directly controlling revolutions per minute (rpm) and torque of the expander (4). As such, it is a continuous variable transmission and there is no need for a gearbox.
• the heat transfer liquid is water or more preferably a water based antifreeze (having freezing point -50°C).
• Working temperature of ambient heat exchanger (9) is adjusted by using a controlling device (not shown) to adjust the rpm of the circulation pump (8), which in turn controls the flow of water in circulation.
• the cryogenic working fluid In the first stage cycle is made up of several thermodynamic processes, when the cryogenic working fluid is in the vaporiser (1), it absorbs ambient heat energy in the vaporiser (1) and expands into the high pressure vapour. This process (isobaric absorbing heat process) is a spontaneous heat transfer or exchange process and therefore no mechanical work is consumed.
• the high pressure vapour flows into the expander (adiabatic expansion process) it outputs mechanical work (expansion work) and refrigeration capacity which means that its specific work is large.
• the at least one high pressure working fluid pump isentropic compression process raises the pressure of fluid and pumps it back into the vaporiser (1), some push work is consumed.
• liquid state cryogenic working fluid almost has no compressibility, its pressure is easy to rise and so it consumes push work from the pump (6) which means that the specific work is less.
• the work consumed by the cryogenic working fluid pump (6) is only 5% of the work that is outputted by the expander (4).
• the circulation pump (8) and fan (10) of the second stage cycle also consumes push work so that the specific work is less. According to the theoretical calculations, it is around 1% of the work output by the expander. Therefore, there is still a large network output from the expansion work of the expander (4) to be consumed by working fluid pump (6), circulation pump (8), fan (10), electrical controls etc.
• the mechanical work output from the expander (4) has exergy of 100%, that can be converted into electrical energy, thermal energy or other forms of energy for use. Because of a dissipation effect, the different types of energy such as mechanical energy, electrical energy, thermal energy etc will all be dissipated into the atmosphere as "waste heat" after being used.
• the atmospheric thermal energy will be reclaimed and used by the invention, therefore realising a "Thermal Energy Recycling Method" which conserves thermal energy by having no increase or decrease in thermal energy. This pioneers a new era of free and easily attainable, green and inexhaustible energy.
• the liquid state working fluid crated by the expander (4) will be cryogenic, so that corresponding heat exchange technology and devices can then be applied to obtain "Refrigeration Capacity's Use in Divided Stages" (For example: air conditioning 21°C ⁇ 25°C, storage 8°C, refrigerating 4°C, freezing -4°C ⁇ -80°C, cryogenic uses -120°C ⁇ -160°C, liquefying air -186°C ⁇ -210°C).
• the invention also has dehumidifying capability. All air contains moisture. When air directly exchanges heat with cryogenic working fluid, it is easy for frost to form on the surface of the heat exchanger (9). Frost will obstruct heat conductibility and causes heat exchanging efficiency to fall. As more and more frost forms, the heat exchanger will be complete failure.
• frost frost-free Two Stage Cycle
• Thermodynamic - Refrigeration System is designed to solve this problem.
• Water has large specific heat and flows easily.
• Cryogenic working fluid is used to exchange heat with water, then water is used to exchange heat with air, thus constituting the "cryogenic working fluid - water -air" two stage heat exchange method.
• Water temperature is directly proportional to the amount of heat exchanged but is inversely proportional to the amount of flow.
• the amount of heat exchanged is directly proportional to the size of work output. When determining the size of work output, the amount of heat exchanged can not be adjusted however the flow of the water circulation can be adjusted. The flow can be adjusted to reach the required water temperature to ensure that the water in the circulation does not freeze and also that no frost forms on the surface of the heat exchanger.
• low freezing point such as -50°C
• Example 1 Using Liquid Nitrogen as a working fluid
• Liquid Nitrogen can be used as a working fluid (see Figures 1 , 2 & 3). According to nitrogen's thermodynamic table of properties,
• FIG. 3 is the graphical representation of the above data.
• This high pressure vapour also fills storage tank (7) and piping (2).
• the high pressure vapour then flows along piping (2) and through the valve (3) into high pressure expander (4) where it carries out adiabatic expansion and propels the piston wheel of the expander (4) to turn which outputs work and refrigeration capacity.
• the pressure of the high pressure vapour falls to 0.1 Mpa (P2)
• temperature of the vapour proportionally falls to 76K (T2).
• the vapour undergoes gas to liquid phase change and liquefies to form cryogenic liquid nitrogen.
• Nitrogen gas can be seen as ideal gas, calculated according to ideal gas adiabatic expansion state equation;
• cryogenic liquid nitrogen's pressure is then raised and pumped by high pressure working fluid pump (6) back into the vaporiser (1) at a pressure of 12 Mpa , where it is undergoes isobaric absorbing heat process and expand into a high pressure nitrogen vapour at 6.6 times the previous volume and the pressure at 12Mpa.
• This process repeats to form "cryogenic working fluid thermodynamic - refrigeration cycle" or "the first stage cycle".
• the high pressure expander (4) outputs mechanical work and refrigeration capacity, which is the expansion work which means that its specific work is large.
• the high pressure working fluid pump (6) consumes work but because liquid state working fluid almost has no compressibility, the work consumed is push work , the specific work is less, according to theoretical calculations, is 5% of the work output by the expander (4).
• the energy consumed by the circulation pump (8) and fan (10) used in the second stage cycle is also push work which according to theoretical calculations is around 1% of the work output by the expander (4). For example, to design an apparatus with an ensured work output rate of 20k W, work theoretical calculations is as follows:
• Net work output expander work output - working fluid pump energy
• the P-h diagram of Figure 3 shows that the first stage cycle is a continuous self sustaining process.
• the enthalpy of the high pressure gas from air heat energy is converted into mechanical work by expander (4).
• the temperature usually ranges between -30° C to +35°C. Even in colder regions (for examples where the temperature is -50°C), there is still a large temperature difference between liquid nitrogen (at -196°C) and air, therefore the liquid nitrogen can still absorb air heat energy, vaporise and expand into high pressure vapour and do work. If used in summer, not only will energy be generated but at the same time the refrigeration and air conditioning functions are also easily obtained, thereby pioneering green and free refrigeration and air conditioning.
• T2 temperature of working fluid after it has expanded adiabatically should fall within this its liquefaction temperature range. If not, primary pressure (PI) will be too high,
• T2 down will be too low and T2 will surpass liquefaction temperature range (for example, N2, 63.151K ⁇ 77.355K) and enter into solidifying temperature range
• the invention is able to use natural single atom gas (for example Nitrogen, Helium etc) and natural mixtures of these gases (for example air) and also double atom gases (such as C02) as working fluid.
• natural single atom gas for example Nitrogen, Helium etc
• natural mixtures of these gases for example air
• double atom gases such as C02
• the heat exchange system can use water based antifreeze (having a freezing point of -50°C) as heat transfer liquid and the temperature of cold air that leaves the heat exchanger (9) be adjusted to use for the following functions: for cooling electronic equipments such as CPU, for air condition (at approximately 20°C to 25°C), for cooling storage (at approximately 8°C to 14°C), for refrigeration (at approximately 4°C), for freezing (at approximately -8°C to -25°C) etc.
• water based antifreeze having a freezing point of -50°C
• the first stage cycle uses the dry air that directly exchanges heat with cryogenic working fluid in the vaporizer.
• the resultant cold air after the temperature adjustment can be used for freezing (at approximately -60°C to -80°C), materials treatment, cooling of machining, freeze grinding (at approximately -120°C to -160°C) etc. It can also be used to directly liquefy air (at approximately -196°C).
• the mechanical work output by the high pressure expander (4) has exergy of 100% and can be used as the power source for all mechanically powered machinery or machineries such as but not limited to vehicles, ships and aircrafts.
• the mechanical work output by the high pressure expander (4) can be further converted into electricity, thermal energy and other types of energy for other uses.
• the invention can provide 10KW to 20KW apparatus per household or business which can be used to provide power, refrigeration, air condition and fresh water making needs.
• the size of the components and the overall cold state engine or apparatus can be designed according to use.
• the cold state engine or apparatus of the invention can be designed as a micro-generator device for powering electronic devices (for example computers, cell phone etc), robots, outdoor equipments etc.
• Thermal energy recycling After the air heat energy has been converted into work output by the expander (4), it can further be converted into electricity, heat or other types of energy for use. Because, of the dissipation effect, they will be turned into waste heat and emitted into the atmosphere. The atmospheric thermal energy can be utilised again by the invention, therefore creating the "Thermal Energy Recycling Method". In this way, the cold state engine or apparatus will neither increase in total amount to exacerbate global warming, nor does it deplete, which completely solves energy source shortage and pollution problem.
• the invention can be used to make fresh water from the air.
• the air heat exchanger (9) should be specifically designed with the requirements of good air flow, highly efficient heat exchange and convenient collection of condensate.
• the reaching of the dew point temperature and maximum condensation of the air moisture can be obtained by adjusting the working temperature of the heat exchanger by the air humidity.
• High quality fresh water can be obtained by purifying and/or mineralising the condensate collected.
• a domestic model of the invention (20KW model) working under the room temperature of 25°C, relative humidity of 70% (Humidity of air: 14g/Kg), heat exchange temperature difference of +/- 20°C can produce a fresh water at the rate if 48Kg per hour.
• the waste water will be released into the environment again because of evaporation and will rejoin the water cycle.
• the air moisture will be harnessed again by the air heat exchanger of the present invention thereby pioneering the method of directly producing fresh water from the air, which completely solves fresh water shortage problem.
• the apparatus of the present invention can be used to cycle air to reach the required humidity, thus obtaining the dehumidifying function.
• the invention focuses on the atmosphere as the main heat source.
• the second stage cycle which is a closed system can be changed into an open system. That is to say, the entry port of the circulation pump (8), can be connected directly to the water source and that water can be circulated to the vaporiser (1) for heat exchange.
• Such designs can be suitable for ship or other maritime use.
• the expander (4) used in the above first stage cycle will now be described in detail.
• the piston wheel expander shown in Figures 4 to 11 is one embodiment of the aforementioned high pressure expander (4).
• FIGS. 4-11 show various components of the expander.
• the expander (4) consists of an outer cylindrical casing (17), ends (18), gasket ring (65) having U-shaped cross-section (19), piston wheel (20), band shaped sealing ring (21, 2 ), shaft (52) etc.
• the expander includes at least one working fluid inlet (23) and outlet (24) on the casing (17), connection tubes (25) and support (26).
• Working fluid inlet (23) and outlet (24) that connect to the casing (17) at a tangent and the diameter of a base (27) of the inlet (23) and the outlet (24) are larger in diameter than the diameter of their respective entry and exit point. Having such a larger diameter at the base (27) allows the working fluid to enter and exit more effectively as well as enhances a start thrust.
• each end (18) of the expander (4) has a bearing (28) and bolt holes (29) and the convex base structure (30) on the ends (18).
• the convex base structure (30) of ends (18) can be seen more clearly in Figure 6.
• the band shaped sealing ring (21 , 21 ') when more than one band shaped sealing sing (21, 2 ) are assembled together they can be considered to be circles of beehive shaped chambers.
• the convex base structure (30) is to be embedded into the ends (18) of the casing (17) for stable placement and sealed to ensure highly accurate concentricity.
• the structure of the gasket ring (65) which includes U shaped cross section can be seen clearly in Figures 11(a) and (b).
• the piston wheel (fig. 5) will now be described in detail.
• the outer circumference of the piston wheel (20) has three circles of piston chambers (31) as seen in Figure 5 & 6.
• piston chamber (31) and inner piston chamber (32) can be formed as one big single cylindrical chamber that is circumferentially located around the piston shaft (52). It may also be possible that there is no inner piston chamber (32) and piston chamber (31) in each circle of piston chambers can extend all the way to or near the piston shaft (52).
• Connection tubes (25) connect the three circles of outer piston chambers (31) in series to obtain sufficient displacement for high pressure expander's isometric working process.
• the piston chamber's (31) outer circumference has sealing ring grooves (33) as seen in Figures 5 & 6 for at least one inner band shaped sealing ring (21, 21 '). As shown in Figures 9 & 10.
• each single piston chamber's (31) volume (V) should be as small as possible (that is to say, when designing, the quantity of piston chambers can be arranged as many as possible and as the quantity increases, single volume proportionally decreases).
• the thrust side's area (A) needs to be as large as possible and the length (L) of the side need to be as long as possible.
• H (enthalpy) U+PV
• W (Work) FS
• V, F, A and other parameters can be selected accordingly when designing model of the invention.
• Figures 9(a) -(c) shows a first example of a band shaped sealing ring (21) of the first type that is formed by number of substantially square shaped seal links (35) each having square shaped slots or apertures.
• the seal links (35) are connected in a jig saw like way.
• the outer circumference of the piston chamber (31) has sealing ring grooves (33) as shown in Figure 5 & 6.
• the links (35) should be fitted one by one into the groove (33) to form a circle.
• Each circle of the piston chamber (31) is matched with the circle of band shaped sealing ring (21) formed by number of shaped links (35).
• the outer diameter (Rl) of the band shaped sealing ring (21) shown in Figure 9 is substantially same as the inner diameter (R2) of the casing (17) and as shown in Figure 6. As such, the exterior of the band shaped sealing ring (21) tightly abuts the interior of the casing (17) and as shown in Figure 6. Similarly, the inner diameter (R3) of the band shaped sealing ring (21) shown in Figure 9 and the diameter (R4) of the circumference surface of the piston chamber's (31) sealing ring groove (33) shown in Figure 6 are substantially the same.
• the two ends of the seal links (35) has stabilising tenon (36) that is adapted to be fitted into the mortise (37) (see Figure 5) thereby ensuring that the number of seal links (35) in the band shaped sealing ring (21) do not dislocate during operation.
• the inside of the seal links (35) has a perimeter self sealing groove (38) as seen in Figure 9.
• the inside wall of the self sealing groove (38) of the seal links (35) has a slightly protruding spring leaf or thin wall (39, 40).
• the thin wall (39, 40) of each seal links (35) will lie flat and tightly against the circumference surface of the piston chamber's (31) sealing ring groove (33).
• the high pressure gas will fill up the piston chamber (31) and the self sealing groove (38) of each of the seal links (35) of the band shaped ring (21) will also be filled by the high pressure gas.
• the top, down and outside of the self sealing groove (38) of the seal links (35) will be pushed to lie against each other, thereby achieving excellent flexible self sealing property.
• the outer circumference (42) of the seal links (35) has been called a friction surface. If after the long term running of the apparatus, there is wear on the friction surface (42) of the seal links (35), this will lead to deviations in the high precision measurement of components.
• FIG 10(a) - (c) shows a different type of band shaped sealing ring (2 ).
• this band shaped sealing ring (21 ') of Figure 10 is a single piece of processed metal.
• the outer diameter (R5) of the band shaped sealing ring (21 ') and the inner diameter (R2) of the casing are substantially the same.
• the inner diameter (R6) of the band shaped sealing ring (21 ') shown in Figure 10 and the diameter (R4) of the circumference surface of the piston chamber's (31) sealing ring groove (33) shown in Figure 6 are substantially the same.
• the structure of the band shaped sealing ring (2 ) is similar to the structure of the band shaped sealing ring (21) of Figure 9. Similar to square shaped apertures in the seal links (35) forming square shaped apertures uniformly in the band shaped sealing ring (21) of Figure 9, there are square shapes apertures that are uniformly formed on the circumference surface of the band shaped sealing ring (21) as shown in Figure 10.
• the band shaped sealing ring (21 ') is a split ring having two ends connected by joints or connectors.
• the joints or connectors are in the form of mortise (47) in one end and tenon (46) in the other end.
• each of the two sides of the interior of the mortise (47) of the band shaped sealing ring (2 ) also have flexible spring (48) being fitted which after the installation pushes tightly against the tenon (46). This will have excellent self sealing property under the fluid pressure and can eliminate any leaks from the gap between mortise (47) and tenon (46).
• the band shaped sealing ring (21 ') has many half circle shaped stabilising keyholes (50) at two sides of one end.
• the wall surface of the piston chamber's (31) sealing ring groove (33) can also have half circle keyholes (so that after the installation of band shaped sealing ring (2 ), the half circle shaped stabilising keyholes (50) will form a perfect circle (not shown)) with the corresponding half circle key holes on the wall surface of the groove (33).
• the piston wheel shaft (52) has two ends (53 and 54) that extends outwards, with one end (53) being used to drive high pressure working fluid pump and the other end (54) used to output work. This design of the expander (4) is convenient and compact.
• the vaporiser (1) uses finned tubes (55) located inside a high pressure shell structure (57). Because the vaporiser (1) in the context of the present invention is used under cryogenic and high pressure conditions, all the components of the vaporiser (1) should be made out of a material that is able to withstand cryogenic temperatures and high strength. The examples of such materials are cryogenic steel, stainless steel, high strength aluminium alloy etc.
• the finned tubes (55) can include high heat conductible material such as cooper, aluminium alloy etc having high pressure ends (56) and high pressure shell (57) that are assembled in a cluster structure (58) by welding.
• the ports for entry (59) and exit (60) on the top and bottom of the two side of the vaporiser (1) are for the heat transfer liquid used or to be used in the second cycle described before.
• the ports for entry (61) and exit (62) on the top and bottom of the other side of the vaporiser (1) are for the cryogenic working fluid used or to be used in the first cycle described before.
• the high pressure cryogenic working fluid such as liquid nitrogen (at 62.15K- 77.35K , 12MPa )flows inside shell (57) side
• the exterior of finned tubes (55) will need to bear pressure, akin to the working stress bearing arches. This way the finned tubes (55) functions in pressure bearing with a larger heat transferring surface area.
• Low pressure heat transfer liquid such as water or water based antifreeze m at ⁇ 0.2Mpa flows through the inside of the finned tube (55).
• the interior wall of finned tube (55) has small heat transfer surface area but because the specific heat of heat transfer liquid such as water is large, it will flow easily and the amount of heat transferred is large. Thus the gas ⁇ liquid heat exchange method constructed this way is relatively more harmonious. As a result, there is excellent heat exchange.
• Air heat exchanger (9)
• I- warm vapour with phase being gas, temperature of 300K and pressure of 12MPa, density 112.88kg/m3 and heat energy of 291.94 kj/kg
• phase II- cryogenic liquid with phase being liquid, temperature of 76K and pressure of 0.1 MPa, density 812.8kg/m3 and heat energy of -124.86kj/kg
• III- cryogenic liquid with phase being liquid, temperature of 82K and pressure of 12MPa, density 810.9kg/m3 and heat energy of -105.82kj/kg
• V In between the vaporiser and expander, V can be approximately equal to I, and in between the working pump and vaporiser, IV can be approximately equal to III
• Expander outputs mechanical work that is continuously variable transmission
• a vaporizer designed to work in cryogenic and high pressure working conditions
• g) Can use air heat energy to output mechanical work, refrigeration capacity and fresh water
• the invention can be used on land, in the air and in sea during all seasons m)
• the invention can also use water heat energy
• the invention can be used for large industries and closed heat energy recycling o)
• the invention can also be used to supply households with power, water, refrigeration and air conditioning.
• piston chamber and inner piston chamber can be formed as one big single cylindrical chamber that is circumferentially located around the piston shaft. It may also be possible that there is no inner piston chamber and piston chamber in each circles of piston chambers can extend all the way to or near the piston shaft.
• the high pressure expander (9) is designed to output mechanical work, which can be directly used to power vehicle, ships, aircraft and various machines, or can be converted into electricity or thermal energy.
• the apparatus can be designed to be as large or as small as required, can be manufactured to be a portable electricity generator, a large scale power station, or can be manufactured to be a generator equipped for each household to supply power, refrigeration and air conditioning, and water.
• the apparatus can be modified for concentrated and heavy users of power such as steel plants, cement plants etc, using closed thermal energy recycle method.
• the apparatus can use the heat energy in bodies of water (such as rivers, lakes and oceans) to do work, thus it can be made into apparatus to power ships and submarine.
• the high pressure working fluid or substance's working displacement length is designed according to when the final pressure (P2) of the expander's outlet is near zero.
• outer piston chambers (31) and inner piston chambers (32) are shown there can be any number of chambers with as many slots as desired. Minimally the inner piston chambers 32 may not be necessary whereby there may only be the piston chambers 31.
• the number of band shaped ring members (21, 2 ) can also be varied to suit particular needs.
• thermometers Any number of pumps, fans, inlets, outlets, valves and thermometers are possible.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Biodiversity & Conservation Biology (AREA)
• Life Sciences & Earth Sciences (AREA)
• General Life Sciences & Earth Sciences (AREA)
• Oceanography (AREA)
• Sustainable Development (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Separation By Low-Temperature Treatments (AREA)
• Filling Or Discharging Of Gas Storage Vessels (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=48429930

Family Applications (1)

Country Status (9)

Families Citing this family (16)

Citations (4)

Family Cites Families (17)

• 2011
  • 2011-11-16 NZ NZ596481A patent/NZ596481A/en unknown
• 2012
  • 2012-11-15 CA CA2891826A patent/CA2891826C/en active Active
  • 2012-11-15 WO PCT/NZ2012/000211 patent/WO2013073972A1/en active Application Filing
  • 2012-11-15 EP EP12850367.9A patent/EP2780590A4/de active Pending
  • 2012-11-15 AU AU2012337470A patent/AU2012337470A1/en not_active Abandoned
  • 2012-11-15 CN CN201280055288.1A patent/CN103930672B/zh active Active
  • 2012-11-15 JP JP2014542270A patent/JP2015502482A/ja active Pending
• 2014
  • 2014-03-20 US US14/220,903 patent/US9347437B2/en active Active
  • 2014-04-30 IN IN3442DEN2014 patent/IN2014DN03442A/en unknown
• 2017
  • 2017-03-26 AU AU2017202013A patent/AU2017202013B2/en active Active

Patent Citations (4)

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events